Running register



June 21, 1938. F. s. SHIELDS 2,121,105

RUNNING REGISTER Filed July 6, 1936 9 Sheets-Sheet l IN VENTOR.

b n ,Trank 513111161618 ATTORNEY.

June 21,- 1938. F, s. SHIELDS RUNNING REGISTER Filed July 6, 1936 9 Sheets-Sheet 2 INELNTOR. frank s. .Sluelds ATTORNEY.

June 21, 1938. F. s. SHIELDS RUNNING REGISTER Filed July 6, 1936 9 Sheets-Sheet 3 INVENTOR. QSF'rank S. Shields BY Z E Z ATTORNEY.

June 2.1, 1938. F. s. SHIELDS RUNNING REGISTER Filed July 6, 1956 9 Sheets-Sheet 4 IN VEN TOR.

frank $.61: ields BY Z N i ATTORNEY.

June 21, 1938. F. s. SHIELDS 2,121,105

I RUNNING REGISTER Filed July e, 1956 9 Sheets-Sheet 5 myENToR. frank S. Sh aelds BY Z Z ATTORNEY.

June 21', 1938. F. s. SHIELDS 2,121,105

' RUNNING REGISTER Filed July 6, 1956 9 Sheets-Sheet 6 E m x k m b Q I l m N l 5;, 1

I ll

' II \IVENTOR. frank 8. Sh zezd ATTORNEY.

June 21, 1938.

F; s. sl-uELDs [RUNNING REGIsTEfi Filed July 6, 19:56

9 Sheets-Sheet 7 qWENToR. Jrank ,3. Shaelds ATTORNEY.

June 21, 1933.

I F. s. sw ms I 2,121,105 'RUNNING REGISTER 9 Sheets-Sheet 9 Filed Jl lly e, 1936 INVENT-OR. I

- ,J-rank (S./$hzleld BY i 3 .1

ATTORNEY.

Patented June 21, 1938 UNITED STATES RUNNING REGISTER Frank S. Shields, Jamaica, N. Y., assignor to S. & S. Corrugated Paper Machinery 00., Inc., Brooklyn, N. IE2, a corporation of New York Applicatio July 6, 1936, Serial No. 89,017

20 Claims. (Cl. 74-395) iis invention relates to registering mechanisms and more particularly relates to novel methods of and apparatus for angular and axial adjusting means for rotating members.

Machines which operate upon advancing sheet material, for example corrugated board, box blanks and the like, generally comprisea plurality of revolving members which perform successive operations upon the sheet. These machines are adjustable for. different sizes of the product and the drums areapproximately set into registering position while the machine is at rest. Accurate registration of the drums, particularly of the multi-color printing and the slotting drums, is not feasible except after test runs upon the material are made.

To expedite the accurate angular and axial alignment of the successive drums, prior registering devices have been developed to perform the adjustments while the machine was in operation in order to avoid starting up and stopping. An important advantage of running registering devices is that rapid compensation for speed changes and slippage of any particular drum or of expansion or contraction of the product due to elasticity or other changes therein may be readily effected while the machine is maintained in operation.

The prior running registering devices included clutches and manual hand adjusting operations which were necessarily slow and inconvenient. I contemplate a running register mechanism which dispenses entirely with clutch engagementor. disengagement of therotating drum and maintains a positive driving connection between the rotating drum. and its motive power. The registering adjustments of my present invention are performed semi-automatically. In the preferred form of my present invention, an individual reversible motor for each drum is used, the direction of rotation of the motor determining the sense of the registering adjustment.

This invention is in the nature of an improvement of my co-pending application Serial No. 75,705, filed April 22, 1936. i The angular registration of this invention is effective over 360 in a clockwiseor counterclockwise sense. The axial registration is effective in either direction over the predetermined distance of control. In one embodiment of this invention, particularly for printing cylinders, the axial and angular control features are embodied in a common registering mechanism operated from a reversible motor by hand lever controls. In another form of this invention, particularly for slotter heads, the angular registering portion alone is embodied in a semi-automatic 360 control.

The registration of each drum is preferably percomplished in my present invention by surround-, ing the registering mechanism with a sleeve which is connected to the internal mechanism which connects to the drum shaft by a worm gear arrangement to complete the positive driving connection from the drum shaft and the motive power. The angular and axial displacements of the drum shaft with respect to the external sleeve is effected by causing the rotation of a corresponding worm operating upon a worm gear cut into a sleeve, in a manner to be described in detail.

' Slotter heads are generally adjusted axially before the machine is started up and circumferential adjustment alone is usually necessary during operation. My present invention is applicable to angular registration without the axial adjustments and accordingly, I disclose hereinafter a preferred embodiment of such an application.

It is accordingly an object of my present inven-' tion to provide novel methods xpf and apparatus for running registration of rotating drums. I

Another object of this invention is to provide a novel running register which maintains a positive driving connection between the motive power and the rotatable drum.

A further object of this invention is to provide a novel semi-automatic running register for optional angular or axial drum adjustment.

Still a further object of this invention is to provide a novel semi-automatic running register for angular adjustment.

Another object of this invention is to provide a novel semi-automatic running register fisotive over 360 in either a clockwise or counterclockwise direction.

These and other objects of this invention will become evident in the following description taken in connection with the drawings, in which:

Figure 1 is a side elevational view of a preferred embodiment of a machine containing two printing cylinders and one registry control slotter in series, as viewed from the drum side of the machine.

formed while the machine is running slowly so Figure 2 is an elevational view from the discharge end, broken through the central portion.

Figure 3 is a diagrammatic illustration showing the inter-relation between the various rollers and the gearing system therefor.

Figure 4 is a vertical cross-sectional view through a preferred embodiment; for the printer drum registry mechanism in accordance with my present invention, and is taken along 44 of Figure 1.

Figure 5 is a cross-sectional view taken along 5-5 of Figure 4 illustrating the novel gearing arrangement for the circumferential adjustment of the printer drum.

Figure 6 is the cross-sectional view taken along 66 of Figure 4 illustrating the novel gearing arrangement for the axial alignment of the printer drum.

Figure 7 is an end view of the printer drum adjustment control with the central housing removed, showing the operating levers and is a cross-sectional view taken along |l of Figure 4.

Figure 8 is a cross-sectional view taken along 8-8 of Figure 4.

Figure 9 is an enlarged detail sectional view of a portion of Figure 8.

Figure 10 is a cross-sectional view taken along the broken line Ill-40 of Figure 4 through details of the printer drum adjusting mechanism, the mechanism being in disengaged position.

Figure 11 is a slightly enlarged view corresponding to Figure 10 with the adjusting mechanism in engaged position.

Figure 12 is a side elevational view of the individual printer drum adjusting mechanism motor, and lever control.

Figure 13 is the cross-sectional view taken along l3-l3 of Figure 10.

Figure 14 is, the. cross-sectional view taken along I4-I4 in Figure 10.

Figure 15 is a vertical cross-sectional view taken along l5--| 5 of Figure 1, through a preferred embodiment of the circumferential adjusting mechanism for the slotter head, being a modification of the printer registry mechanism and corresponds to Figure 4.

Figure 16 is a. cross-sectional view taken along iii-l6 of Figure 15 illustrating the novel gear arrangement for the circumferential adjustment and corresponds to Figure 12 of the printer adjusting mechanism.

Figure 17 is the cross-sectional view taken along l'i-l'| of Figure 17.

Figure 18 is the cross-sectional illustration taken along I8-l8 of Figure 15.

The description of this invention starts with the preferred printer-slotter machine taken as a whole, then proceeds to the adjusting mechanism for the distance between each of the coacting rolls operating on the stock, then a preferred embodiment of the axial-angular registering mech-- anism as applied to the printing cylinders is described, continuing with the description of a slotter head register having only angular control.

Description of the printer-slotter machine Referring to Figure 1, the sheets of corrugated board 20 are stacked in position upon the machine and the back gauge 21 is adjusted for the pile of sheets 20. A table 22 is provided for the input end of the machine. The sheets are automatically fed successively into the machine and a pair of guide plates 23 are used to keep the sheets centralized in a manner well-known in the art.

The machine of my preferred embodiment is shown with two printing drum sections 24 and 25, and one slotter section 26, arranged in series from right to left. The printing drums 24 and 25 are used for printing in two colors upon the sheet passing through the machine. Ink-wells 21 and 28 are provided for the printing drum sections 24 and 25 respectively.

Hand adjusting mechanism 30 is provided for controlling the distance betweenthe first or input pair of feed rolls and extends transversely through the machine, and has an independent control wheel 3i on the opposite side of the machine, as seen in Figure 2. The position of the presser roller with respect to the printing cylinder of section 24 is manually controlled by hand wheel mechanism 34; the position of the presser roller co-acting with the printing cylinder of section. 25, by adjusting wheel mechanism 32. The distance between the feed rollers located between sections 24 and 25 is manually controlled by the hand wheel mechanism 33; the distance between the feed rollers located between the printing section 25 and the slotter section 26, by the hand wheel adjusting mechanism 34'. Hand wheel adjusting mechanism 35, located beneath the slotter control mechanism is provided to adjust the position of the female slotter shaft with respect to the main slotter head. Hand wheel adjusting mechanism 36 is provided for adjusting the position of the creaser and trimmer lower shaft. The plurality of hand wheel adjusting members 30 to 36 are used for adjusting the machine in accordance with the thickness of the stock being fed therethrough as will be evident to those skilled in the art.

The printer slotter machine of my preferred embodiment is driven by a synchronous motor located within the motor housing 31. The machine has an adjustable speed drive which is controlled by the hand wheel 38 which operates a Reeves pulley connected between the synchronous motor and the gearing system of the machine. It is to be understood that a, different type of drive for the machine is feasible.

The printer slotter machine of my preferred embodiment is built in two separable sections, the first section contains the right end of the machine including the motor drive, the sheet stacking and feeding mechanism and the first printingcylinder; the second section comprises the remainder of the machine including the second printing cylinder, slotter, and the creaser and trimmer wheels. The right end section is movable on a set of tracks 40. Hand lever 4| is operated to separate the machine into its two major sections, the right end section being readily slidable on the tracks 40 when the lever 4| is in proper position. A stop post 42 is provided at the edge of the machine to prevent the movable section from sliding off the tracks 40. The separation of the machine between the printing sections 24 and 25 is provided to permit a person to enter therebetween and prepare the printing cylinders for operation. The removable type is mounted upon each of the wooden printer cylinders of the sections 24 and 25. A hand wheel 43 is used to lock the sections after they are brought together.

The printer slotter machine is also provided with automatic forced feed lubrication for all the parts which require lubrication. An oil gauge 44 is used to indicate the lubrication oil supply.

Figure 2 is a view of the printer-slotter machine from the discharge end as seen from the hereinafter.

by small individual motors.

slots upon the advancing stock in a manner well known in the art. The slotter heads 41 and 48 are rigidly adjustedam their proper axial position on their common shaft. The circumferential adjustment of the slotter heads is performed by the novel adjusting mechanism forming the basis of the present application and described in detail The vernier adjusting mechanism for the slotter section 26 is contained in housing 58 at the right end of Figure 2 and is driven by the electric motor 5|. Adjacent housing 52 behind slotter control housing 50 encloses the longitudinal and circumferential adjusting mechanism for the printing cylinder of section 25, and

another similar section located further behind this section is provided for the other printing cylinder. v

The creasers 53 and 54 together with the trimmers 55 and 56 are located at the very end of the discharge section and are the last to operate upon the advancing stock. The creasers and trimmers are mounted upon two common steel shafts 51 and 58. The coacting members of the creasers 53 and 54 are mounted upon their re spective shafts 51 and 58; and the co-acting members of the trimmers 55 and 56, are also mounted upon these shafts. The axial position of the trimmers 55 and 56 correspond to the size of the sheets required.

The creasers and trimmers require only the initial axial adjustment corresponding to the desired width of the stock and the distance between the creases. The creasers and trimmers do not require any angular adjustments since they are circular tools. The slotter heads 41 and 48 are pre-set in their axial position and require circumferential adjustment to, accurately position the slotting operations upon the advancing sheet. Suitable novel semi-automatic circumferential adjusting mechanism for the slotter section 26 is described in detail hereinafter. cylinders of printing sections 25 and 26 require both circumferential and axial adjustment since the two color process must be accurately imprinted upon the advancing sheet. Accurate registration of the cylinders is accordingly essential. Novel semi-automatic axial and circumferential adjusting mechanism is provided for the printing sections and is described in detail hereinafter. v

The electric motor enclosed by its housing 31 is located at the left side of Figure 2. The Reeves pulley variable speed drive is enclosed in housing 68 adjacent the synchronous motor housing 31. The drive motor together with the Reeves drive, operates the gearing system which drives the printing sections'24 and 25 and the slotter-creaser-trimmer section 26. The registry mechanism for the printer and the slotter sections in my preferred embodiment are driven The individual motor for the slotter registry mechanism is shown as 5| in Figures 1 and 2. The motor for the printing section 25 is shown as BI, and the motor for the printing section 24 is 62.

Figure 3 is a diagrammatic showing of the arrangement of the plurality of co-acting rollers The printing of the printer-slotter machine together with the gearing system therefor. The gears are illustrated in a dot and dash line and the other parts, such as the rollers, drums and slotters are illustrated in dotted lines. The orientation of the diagram corresponds to the position of the machine as viewed in Figure 1.

The sheets from table 22 are successively introduced between the input pair of feed rolls 85-46 by means of the reciprocating pusher mechanism 61. The sheet passes through the machine along the broken horizontal line 68 schematically indicated on the diagram. The distance between the feed rolls 65-458 predeterminesthe pressure upon the stock. Y The pressure is adjustable by controlling the position of the upper feed roll 65 by means of the hand wheel adjusting mechanism 38 shown in Figure 1.

'roll 1| of the first printing section 24. The pressure upon the stock between the printer cylinder 18 and presser roller 1| is adjustable by means of the hand wheel adjusting mechanism 3| shown in Figure 1', which positions the presser roller 11 along the are 12 in a manner to be described hereinafter. The revolving. printing cylinder 18 prints the required impression of a predetermined color upon the sheet as it advances through the machine. The presser roller 1| maintains suitable pressure betweenthe'stock and the cylinder 18. 1

The sheet then moves between the revolving feed rolls 1314 to the second printing section 25 between the second printing cylinder 18 and its co-acting presser roller 1|. The presser roller 11" is adjustable in position along the are 12' in a manner similarv to presser roller 1|. The bottom 15 and the co-acting female slotter head 16.

The distance betweenthe slotter sections 15 and 18 is adjustable by the hand wheel mechanism 35, shown in Figure 1 along the are 11, the'mechanism being similar to that hereinafter described in connection with presser roller 11. After the slotting operation, the sheet is moved to the creaser-trimmer rolls, schematically indicated by dotted circles 18 and 19 corresponding to the creasers 53-54 and trimmers 55-56'mounted on shafts 51 and 58 as illustrated in Figure 2.

The gear system for the machine is all interconnected and driven by the main synchronous motor hereinabove referred to. Printing cylinder 10 has mounted on its shaft gear 8|] which is interconnected with the gear 88' connected to the second printing cylinder 10' through the intermediate gear 8|. The gear is interconnected with the gear 82 connected to the slotter 15 through the intermediate gear 83. The input feed rollers 65 and 68 are driven from the gear 84' "along the corresponding arcs 12 and 14a preserve steel oscillating roller I02.

The female slotter I6 is driven by gear 03 mesh-- ing with the gear 02 of slotter head-15. Gear 93 drives the gear 94 of female slotter I6 through the intermediate gear 05. Gear 95 also drives the lower creaser-trimmer I9 through its gear 96. Gear 93 drives the upper creaser-trimmer I through its gear 91.

The inking mechanism for the printing sections 24 and 25 are similarly constructed and are herein described in connection with section 24, the second section 25 being labeled with corresponding numerals primed. The ink roller ,I 00 absorbs on its surface, the ink from the ink-well indicated at 21. The ducker roller I M transfers the ink from the surface of ink roller I 00to the The steel roll I02 spreads the ink upon the rubber or composition transfer roll I03 to the steel oscillating roller I04. The ink is evenly spread upon the steel roll I04 and is transferred to the type on the surface of the printing cylinder 10 through the composition transfer rollers I and I06.

The inking cylinders I00 to I00 are driven from the gear 00 through the intermediate gear I01 which drives the steel oscillating rollers I02 and I04 at their respective gears I00 and I09.

Roller pressure adjusting mechanism The rollers of the printer slotter machine are arranged in pairs, for example, the printing cylinders, the feed rollers, the slotter heads 'l5|6 and the creaser-trimmer rollers I0-18. The vertical position of one roller of each pair is manually adjustable to accommodate different stock thicknesses by the hand wheel mechanisms 30 to 36, illustrated in Figure 1. Figure 4, which is a a vertical cross-sectional illustration through the printing cylinder adjusting mechanism illustrates in section the operation of the adjustment for the lower printing cylinder or presser roller II.

The hand wheel 3i drives a worm IIO which rotates worm gear III keyed to shaft I I2. The worm of worm gear arrangement III-I I2 is encased in a housing II3 attached to one side of the frame section 46. The adjusting shaft II2 extends through the frame 46 .to the opposite side of the machine. Shaft I I2 is supported in bushing H4 in frame member 46. An eccentric cam H5 is keyed to shaft II4 by key 6. A metallic plate I I1 surrounds the eccentric cam I I5 and extends upwardly to support the presser roller II in roller bearing I I0. A washer I I 9 and nut I20 hold the metallic plate H1 and eccentric cam H6 in position upon rod I I2 and against the corresponding surface of frame member 46. Metallic plate II! is movable vertically and its vertical height depends upon the orientation of the eccentric cam II5 which is under the control of the hand wheel 3i which rotates the position of cam H5.

The lower printing or presser roller 'II is rotatably supported in roller bearing II8 set into the adjustable plate Ill at one endof the machine and is supported on its opposite side by a similar structure under the control of the corresponding end of shaft II2. Spur gear 90 is keyed on a shoulder I2I extending from the shaft of presser roller II. The gear 90 meshes with the intermediate gear 89 schematically illustrated in Figure 3.

By proper rotation of the hand wheel 3| in a clockwise or counterclockwise direction, the relative distance between the printing cylinder I0 and the presser cylinder II is obtained. Gear 90 is maintained in constant meshing relationship with its driving gear 89 as illustrated in Figure 3. The hand wheel 3| contains self-locking mechanism which maintains it in a locked condition between adjustments. Both supports of the movable cylinder II are controlled simultaneously so as to maintain the cylinders horizontally and in true parallel relationship.

The adjusting mechanism herein described for the pressure or distance between the co-acting rollers is of similar construction to the illustrated embodiment shown in Figure 4, in conjunction with the printing cylinders 10 and II. The distance between the rollers depends upon the thickness of the stock passing through the machine as well as its compliance.

Printer drum registering mechanism The printing cylinder I0 requires accurate angular and axial adjusting mechanism which functions while the machine is in operation to expedite precise positioning of the printing impressions upon the sheet so that impressions of different colors will be accurately superimposed. In Figures 4 to 14, I have illustrated a preferred embodiment for carrying out the principles of my present invention. Although I have illustrated this mechanism in conjunction with a printer drum, it is to be understood that it is equally applicable to any rotating member which requires circumferential and axial alignment.

The drum I0 is rotated through gear 80 which connects to the shaft I22 through the sleeve I23 and the control mechanism for the drum 10 located within the sleeve I23 as will be evident upon further description of the details of the control mechanism. Shaft I22 of the cylinder I0 is located within sleeve I24 and is free and slidable therein. Sleeve I24 is supported in roller bearing I25 attached to the frame member 46. Sleeve I 24 is rigidly connected to gear 80 as is the housing sleeve I23. Gear 00 is continuously rotated from the gearing system extending from the main drive synchronous motor. The housing sleeves I23 and I24 rotate with the gear 80 as a unitary structure and the registering mechanism located within the housing sleeves rotate therewith in unison to correspondingly positively drive the drum I0. A feature of my present invention is to semi-automatically control the angular or axial position of the revolving drum 10 by superimposing corresponding correcting motions upon the drum while maintaining its positive driving connection to the driving source.

The circumferential adjustment of the drum 10 is effected by the rotation of the shaft I26. Shaft I26 is semi-automatically rotated under the control of the operator in a manner to be described hereinafter. A worm I2! is integral with the shaft I26 and accordingly rotates therewith.

vA sleeve I28 concentric within housing sleeve I23,

has a set of Worm gear teeth I30 cut on its periphery. The worm gear I 30 co-acts with the worm I21. A shoulder I3I extending from the shaft I22 has a key I32 set therein which rides in a keyway I33 cut into the sleeve I28.

Drum 10 accordingly rotates with sleeve I28 under the action of the key I32. The shoulder I3I of the drum shaft is slideable with respect to the sleeve I28 but rotatable therewith. Rotation of shaft I26 will cause the sleeve I28 to revolve and the drum 10 will revolve therewith.

Figure is a cross sectional view taken along 5-5 through the circumferential control mechanism portion of Figure 4. The worm shaft I26 is shown rotatably supported inthe housing sleeve I23 and moves-as a unit as the sleeve I23 rotates. The worm I21 meshing with the worm gear I30 accordingly rotates the sleeve I23 together with sleeve I23. The interlocking relationship between the worm I21 and worm gear I30 causes the sleeve I28 to rotate integrally with the housing sleeve I23 and therefore gear BII. Since the cylinder is keyed to the sleeve I26, it normally rotates in a positive driving relationship with gear 80. However, rotation of the worm I21 will superimpose a rotation clockwise or counterclockwise upon the normally rotating sleeve I28 to correspondingly superimpose the circumferential adjusting motion upon the rotation of the drum 10. It will be evident that the angular correction of drum 10 is effected while maintaining a positive driving connection between the drum 10 and its driving gear 80.

The rotation of worm shaft I26 is under the control of the motor power and mechanism to be hereinafter described, which rotates rod I35 (Figure 5). A worm I36 keyed to rod I35 engages with a worm gear I31 keyed to one end of the worm shaft I26. Rotation of rod I35 will accordingly superimpose a clockwise or counterclockwise motion upon the normally rotating shaft I3I supported within the housing sleeve I23.

The axial adjusting mechanism for the cylinder 10 is under the control of the rotation of shaft I40 as viewed in Fig. 4. Shaft I40 contains integral therewith, 5a worm I 4| which meshes with a worm gear I42 out upon the periphery of sleeve member I43 concentric with the housing sleeve I23. A series of threads is out upon the internal surface of the sleeve member I43 which threads co-act with a threaded sleeve I 44. Threaded sleeve I44 is rotatably mounted upon an extension I45 of the cylinder shaft I22.

Rotation of worm shaft I40 revolves its integral worm I4I which superimposes a corresponding clockwise or counterclockwise motion upon the sleeve I43. Rotation of sleeve I43 coacts with the threaded sleeve I44 to move it to the right or left. Since sleeve I43 is constrained from movement to the right or left, the threaded sleeve I44 necessarily moves axially in response to the'rotation of the sleeve I43.

Threaded sleeve I44 is held from axial movement with respect to the shaft extension I45 by means of a shoulder and a nut and washer at its right end. Axial movement to the right or left of the threaded member I 44 correspondingly moves the cylinder 10 which is otherwise slidably mounted. I

Figure 6 is a cross-sectional view taken through the axial adjusting mechanism of Figure 4. The worm shaft I40 is rotatably supported in housing sleeve I23. Rod I46 controlled by power drive mechanism hereinafter described, is mounted on sleeve I23 and has a worm I41 keyed to it. Worm I41 meshes with worm gear I48 which is keyed to the worm shaft I40. control rod I46 accordingly superimposes a clockwise or counterclockwise rotation upon the sleeve I43 which correspondingly shifts the threaded sleeve I44 to the right or left and accordingly controls the axial position of the cylinder 10.

Rotation of the axial The circumferential and axial control mechanism is actuated by motive power from the reversible electrical -motor 62 under the control of the operator. As viewed in Figure 4, motor 62 is supported upon the casing-I50 enclosing the registering mechanism. A sprocket wheel I5I is keyed tothe shaft I52 of the motor 62. A sprocket chain I53 transmits the motive power to a sprocket wheel I54 coaxial with the cylinder 10. Sprocket wheel I54 is keyed to a shaft I55 supported in roller bearings I56 and I51 in the casing structure.

A friction clutch is used for manually engaging and disengaging the motive power to the registry control mechanism. The inner friction cone member I60 is slideably'keyed to an extension of shaft I55 and its position is controlled by hand lever I62 operating a yoke I69 eoacting with a groove I63 on the hub I64 of friction cone I60. The outer friction cone I6I has a hub portion I 65 which is slideably keyed to sleeve I66 by feather key I61. Sleeve I66 is rotatably mounted by two roller bearings upon a rod I61 integral with and extending from a sleeve I68 keyed to the housing sleeve I23. v I

A helical spring I10, concentric on the hub I65 of clutch member I6I, mechanically biases clutch member I6I away from awasher I1I set against a shoulder of sleeve I 66. The outer surface of friction cone I6I normally engages an annular ring I12 attached to the right end portion of sleeve I 23. When, clutch I 60-I6I is in disengaged position, as illustrated in Figure 4, spring I10 forces the outerclutch member I 6I into engagement with ring I12. Clutch member I6I accordingly rotates together with the sleeve I23 in correspondence with the motion of the gear 80. When friction clutch I60I6I is engaged by hand lever I62, spring I 10 is compressed and clutch member I6I is released from the annular ring I12 and is under the control of the motive power from the, reversible motor 62 as will be hereinafter described in greater detail.

Figure 7 is the sectional view taken along 1-1 of Figure 4 showing the end view of the sprocket drive from the motor 62 to the sprocket wheel I 54. Lever I62 is the clutch engaging and disengaging lever to actuate the circumferential and axial registering mechanism through the friction clutch I60--I6I in a manner to be hereinafter described. The lever I62 is manually held in position during the registering operations and is intermittently operated to effect precise results.

The hand lever I13 is a self-locking lever which controls the axial registering section of the registering mechanism and determines whether the axial movement of the drum 10 will be effected when the clutch lever I62 is in engaged position. Plate I14 attached to the handle of lever I13 permits ready release of the detent locking portion of the lever (not shown) to permit resetting thereof. A similar lever I15 located opposite lever I13 is an independentcontrol for determining when the angular registering portion of the registering mechanism will be actuated if the clutch lever I62 is in engaged position. The operator merely throws lever I13 or I15 (or both) into control position for corresponding control of the circumferential or axial registration of the drum, and then intermittently operates the clutch lever I62 to effect the registration desired.

Figure 8 is the cross-sectional view taken along 83 of Figure 4, being a vertical section through the registering control mechanism. Hand lever I13 which controls the operation of the axial registry mechanism operates a sleeve I16 attached to a rod I11 secured to one end of lever I13. Arms I18I18 extending from sleeve I16 form a yoke which sets into an annular groove in ring I 80. The axial position of ring I80 controls the engagement of a spur gear I8I with the axial control rod I46 in a manner to be described hereinafter. The rod I46 controls the axial registration of the drum 10 in a manner hereinabove described in connection with Figures 4 and 6. Spur gear I8I is normally free to rotate with respect to rod I46 and engages with a central spur gear I82. The spur gear I82 is integral with the sleeve I66 as illustrated in Figure 4. A spur gear 183 rotatably mounted on rod I35 also coacts with central gear I82. As will be hereinafter described, the hand lever I15 (Figure 7) controls, in a manner similar to lever I13, the engagement of the spur gear I83 with rod I 35. The rod I35 controls the angular or circumferential registration of the drum in a manner hereinabove described in connection with Figures 4 and 5.

Figure 10 is a horizontal cross-sectional view taken along I0-I0 of Figure 4 illustrating the mechanism for the operation of the angular and axial control rods I35 and I46 by the motive power imparted to shaft I55 from the associated q A of key I86 abuts the outside edge of a second circular ring I90 corresponding to ring I and mounted adjacent thereto as shown in Figures 10 and 11.

The keys I and I86 control the engagement of corresponding rods I46 and I35 for effecting the control of the related axial and circumferential registering mechanism. Key I85 contains a tongue I 9i which co-actswith an/ annular groove in the hub of positive clutch member I92. Clutch member I92 is 'slideably keyed by key I93 on the end portion of rod I46. Figure 9 is an enlarged view of a corresponding portion of Figure 8, and shows another view of the key I85 with its tongue I9I co-acting with clutch member I 92.

The yoke Ill-I18 (operated by lever I13) controls the movement of ring I80. when ring I80 is moved towards the right, it abuts projections I 81 of key I85 and accordingly moves key I85 towards the right. The tongue I9I of key I85 will correspondingly move clutch member I92 toward the right against the spring action of spring I 84.

Figure 13 is a cross-sectional view taken axially along rod I46 along I3I3 of Figure 10. Rod I46 is rotatably mounted in bushings I95 and I96 set into the housing sleeve I23. The left end of rod I46 has a nut.I91 pinned thereto. The spring I94 at the right end of rod I46 abuts the head I98 of the rod I46 and normally mechanically The metallic ring I80 encircles the of the positive clutch member I92 form a positive driving connection between the clutch member I92 and the spur gear I8I.

The annular groove 20I in clutch member I92 co-acts with the tongue I9I of key I85. key I85 is moved toward the right by ring I80 abutting projection I81, clutch teeth I99 and 200 are disengaged since clutch member I92 is moved against the biasing spring I94. However, when lever I13 moves ring I80 toward the left, biasing spring I94 moves clutch member I 92 along rod I46. A positive engagement of the clutch teeth I99200 is made whereby a positive driving connection is made between spur gear I8I and the rod I46 through the clutch. member I92 keyed thereto. Spur gear I8I accordingly controls the rotation of'worm I 41, keyed by keys 202 to rod I46. Worm I41 meshes with worm gear I48 which is keyed to the shaft I40 which directly controls the axial registering mechanism hereinabove described in connection with Figures 4 and 6.

The engagement of the angular control rod I35 with the spur gear I83 is similar to the hereinabove described relation between the axial control rod I46 and the spur gear I80. Referring to Figure 10, sleeve I90, the position of which is controlled by yoke 203-203, operated by hand lever I15 (Figure 7), abutsthe projection I88 of key I86. When ring I is moved by lever I12 to the right, it abuts projection I88, moving key I86 correspondingly towards the right to the position illustrated in Figure 10. The tongue 209 of key When I86 co-acts with the annular groove of the positive clutch member 204 which is slideably keyed by key 205 on rod I35.

Figure 14 is a cross-sectional view taken through the control rod I35 along I4I4 of Figure 10. A spring 206 set between the head 201 of rod I35 and the clutch member 204, normally mechanically biases the clutch member 204 into engaging position with the clutch teeth 208 integrally cast with spur gear I 83. The tongue 209 of key I86 co-acts with the annular groove 2I0 of the clutch member 204 to axially move the clutch member 204 against the biasing spring 206 to the illustrated disengaged position. When hand lever I15 moves sleeve I90 towards the left,

spring 206 moves the clutch member into engaged position with clutch teeth 208 and the spur gear I83 is correspondingly engaged with slidable' clutch member 204. A positive driving connection and I83, free to revolve upon their respective shafts I46 and I35, are in constant meshing relationship with the central gear I82. It is to be understood that the whole mechanism illustrated within the casing I50 rotates together with the drum 10 when gear 80 revolves. Accordingly, control shafts I 46 and I35 normally revolve in a circular path co-axial with the shaft I22 of drum 10. With clutch I60I6I in disengaged position as shown, the central gear I82 revolves together with the revolving hub I23 since gear I82 is keyed to the hub of the outer clutch cone I61 which engages the annular ring I12, set into the casing I23. Gears I8I, I82 and I83 accordingly rotate 2,121,105 about the drum 10 axis but do not revolve with respect to each other but remain in intermeshed relationship as will be evident to those skilled in the art.

When lever I13 is operated to move the yoke I18-I18.and the ring I80 to the left, spring I94 forces positive clutch member I92 into engagement with the spur gear IBI. s As long as friction clutch I60 -I6I is disengaged, the shaft I46 does not rotate. However, by throwing the friction clutch I 6lI--l6l into engagement by hand lever I62 (Figure 7) operating on yoke Hi9, the outer 'friction cone I 6| moves to the left against the biasing action of the spring I61 away from engagement with the annular ring I12. Figure 11 illustrates the positive clutch member I 92 in engaged position with the spur gear I8I and also the friction clutch I60'-I6I in engaged position. The motive power from shaft I55 is accordingly transmitted directly to intermediate gear I82 which, in turn, rotates the spur gear I8l. Rotation of spur gear I8I operates axial control shaft I46 and the drum 10 moves axially to the right or left in accordance with the clockwise or counterclockwise rotation of shaft I55 in a manner hereinabove described in connection with Figures 4, 6 and 13. The alternate sense of rotation of shaft I55 is obtained by utilizing a reversible electrical motor 62. Rotation of the motor in one direction will correspond to the registration of the drum 10 to the left; and rotation of the motorin the opposite direction, correspondingly to the right.

In a similar manner, the angular registration of the drum I3 is accomplished by throwing lever I15 (Figure 7) to move yoke 2032Il3 together with ring I90 to the left to permit clutch member 204 (to become positively engaged with spur gear I63 under the action of biasing springzos. The

engagement of clutch member 204 with spur gear I83 causes the central gear I82 to drive the angular control shaft I35 in a manner hereinabove described in connection with Figures 4,5 and 14. The angularregistration'is clockwise or counterclockwise inaccordance with the predetermined sense of rotation of the reversible motor 62 which drives shaft I55.

From the foregoing it will now be evidentthat the semiautomatic printing drum aligning mechanism of my present invention permits the axial or angular alignment of the drum to be made from the power of a. reversible motor associated with the printer drum. Figure 12 is an end elevational view of the motor mounted on the control mechanism casing I50 also showing the hand levers I62 and I13 corresponding to the right hand side of Figure 7. The hand lever I13 controls the engagement of the axial control mechanism and when thrown to the dotted position, engages the positive clutch member I92 to place the axial control mechanism in .operative relationship with respect to the 'motor I62. By then operating the friction clutch lever I62 to the dotted position, the motive power for motor 62 will be transmitted through the friction clutch I6Il-.-I6I to the engaged axial control mechanism to effect theaxial movement of the drum 10. On the opposite side of Figure 12 is located the hand lever I15 (see Figure '7) which operates the engagement of the positiveclutch member 204 to place the angular registering mechanism in operative relationship with motor 62. Engagement of the friction clutch by hand lever 162 will cause the angular registration of the drum 1!] in accordance with the sense of rotation of the reversnation of the axial portion thereof.

ible motor 62. It is to be understood that the axial and angular adjustments may be effected simultaneously. However, a more flexible control is had when they are independently operated. Motor I62 may be operated by a control button arrangement by the operator to control its speed and sense of rotation.

slotter-head adjusting mechanism The slotter head, as already described,- requires only an angular registering control in the printerslotter machine. Figure illustrates a preferred ,embodimentfor effecting the angular control of the slotter in accordance with my present invention. This control is similar to the control of the printing cylinders but is simplified by the elimi- The shaft 220 of the slotter'head 15 is rotatably mounted in sleeve 22I which is fastened to a corresponding portion of frame 46 by roller bearing 222.

Gear 82 connected to the gearing system, as illustrated in Figure 3, drives the slotter head shaft 220 through the-housing sleeve 223 bolted to the gear 82 and connected to the shaft 220 through the internal control mechanism. Shaft 224 mounted in sleeve 223 is rotated by mechanical connections to the motor 5| to effect the angular registration of the slotter 15. A worm 225 cast integral with shaft 224 engages a worm gear 226 out into the sleeve 22 1 concentric within housing sleeve 223.

tation of shaft .224 accordingly superimposes a. corresponding motion upon sleeve 221' which effects the angular registration of slotter head 15.

The shoulder 228 extending from shaft 220 is keyed with key 230 to sleeve 221. Ro- I Figure 16 is a cross-sectional view through the angular adjusting mechanism within housing sleeve 223 astaken along l6---II5 of Figure .15.

j Shaft 224 is journalled in housing sleeve 223 and contains a nut 23I pinned to the-right end portion thereof adjacent a washer 232. The left end of shaft 224 has a worm gear 233 attached to it which meshes with worm 234 in turn keyed to angular control shaft 235.

Figure 17, is the cross-sectional view through the control rod 235 taken along I1--I1 of Figure 16. The; control rod 235 is journalled in bushings 236 and 231 set in housing sleeve 223. Worm 234 keyed to rod 235 meshes with the worm gear 233 which controls the shaft 224 which effects the angular registration of, the slotter head 15. A,

spur gear 240 is keyed to one end of control rod 235. The rotation of spur gear 240 will accordingly rotate worm gear 233 by the worm 234 to effect angular registration of the slotter head shaft 228 as will now be evident to those skilled in the art. The motive power for effecting the angular registration is obtained from reversible motor 5| mounted upona base 24l extending from casing 242 enclosing the registering mechanism. The shaft 243 .of motor-5i iskeyed toa sprocket wheel 244 which operates a sprocket chain 245 meshing with .a sprocket wheel 246 keyed to shaft 241. Shaft 241 is supported in roller bearings 248 secured to the housing 249. The extension of rod 241 is secured to the inner friction cone 250 of friction clutch 25Il-25I. Theengagement of v friction clutch 250.-25I 'is controlled .by hand keyed to sleeve 256 rotatably supported about exslotter head shaft 220 upon roller bearings 258. A spur gear 260 is cast integral with the left end of sleeve 256. A spring '25! mechanically biases friction cone member 25l into engagement with an annular ring 262 mounted at the right end of housing sleeve 223, the opposite end of spring 2H abutting a washer 253 set against the gear 250.

Figure 18 is a cross-sectional view taken along l.8 l8 of Figure 15 illustrating the engagement of the gear 260 with the spur gear 240. Gear 240 is directly keyed to the angular control shaft 235 and gear 250 is directly keyed to the outer friction cone 25L When the hand lever 252 throws the friction clutch 25ll--25l into engagement, the clutch member 25! will move away from the annular ring 252 and the gear 250-will be directly rotated by the shaft 241 motivated by the motor 25L Rotation of gear-260 will correspondingly rotate spur gear 240 to effect the angular registration of slotter head 15 in a manner described in'connection with Figures 15, 16 and 17. The sense of the angular correction will correspond to the direction of rotation of the motor when the clutch 250--25I is disengaged, the gears 240 and 260 will merely remain intermeshed not revolving with respect to each other, the outer gear 2" moving in a circular path about the gear 260 which rotates together with the slotter head driven by gear 82.

The angular control is effective over 360 and is effected ina clockwise or counterclockwise diand scope of my present invention and are adaptable to rotating drums in general, and not speciflcally to the machine of my preferred illustration, and accordingly I do not intend to be limited except as set forth in the following claims.

Iclaim:

1. A running adjusting means for a driven shaft adapted to be rotated by a gear comprising: a driving connection between said gear and said shaft including means for angularly adjusting said shaft with respect to said gear, and a housing sleeve secured to said gear; said angular adjusting means comprising an angular adjusting sleeve concentric within said housing sleeve and keyed to said shaft, and means interposed between said sleeves for changing the angular relation between said angular adjusting sleeve and said housing sleeve.

2. A running adjusting means for a driven shaft adapted to be rotated by a gear comprising: a driving connection between said gear and said shaft including means for angularly adjusting said shaft with respect to said gear, and a housing sleeve secured to said gear; said angular adjusting means comprising an angular adjusting sleeve concentric within said housing sleeve and keyed to said shaft, means interposed between said sleeves for changing the angular relation between said angular adjusting sleeve and said housing sleeve comprising an angular adjusting worm gear integral with said angular adjusting sleeve, an angular worm coacting with said angular adjusting worm gear and an angular adjusting worm shaft rotatably mounted on said housing sleeve connected to said angular adjusting worm, and means for controlling said angular adjusting means operatively connected to said angular adjusting worm shaft.

3. A running adjusting means for a driven shaft adapted to be rotated by a gear comprising: a driving connection between said gear and said shaft including means for angularly adjusting said shaft with respect to said gear, and a housing sleeve secured to said gear; said angular adjusting means comprising an angular adjusting sleeve concentric within said housing sleeve and keyed to said shaft, means interposed between said sleeves for changing the angular relation between said angular adjusting sleeve and said housing sleeve and means for controlling said angular adjusting means; said angular control means comprising an angular control rod, an angular control gear rotatably mounted on said angular control rod, and means for establishing a drive connection between said angular control rod and gear.

4. A running adjusting means for a driven shaft adapted to be rotated by a gear comprising: a driving connection between said gear and said shaft including means for angularly adjusting said shaft with respect to said gear, and a housing sleeve secured to said gear; said angular adjusting means comprising an angular adjusting sleeve concentric about and keyed to said shaft, means for changing the angular relation between said angular adjusting sleeve and said housing sleeve, and means for controlling said angular adjusting means; said angular control means comprising an angular control rod, an angular control gear rotatably mounted on said angular control rod, and means for establishing a drive connection between said angular control rod and gear; and means for operating said control means comprising a source of motive power, an intermediate gear meshing with said angular control gear, and means for driving said intermediate gear by said source.

5. A running adjusting means for a driven shaft adapted to be rotated by a. gear comprising: a positive driving connection between said gear and said shaft including means for angularly adjusting said driven shaft with respect to said gear, means for axially adjusting said driven shaft with respect to said gear, and a housing sleeve secured to said gear; said angular adjusting means comprising an angular adjusting sleeve concentric about and slidably secured to said shaft, means for changing the angular relation between said angular adjusting sleeve and said housing sleeve comprising an angular adjusting worm gear integral with said angular adjusting second sleeve, an angular adjusting worm coacting with said angular adjusting worm gear, and an angular adjusting worm shaft connected to said angular adjusting worm journalled in said housing sleeve, and means for controlling said angular adjusting means; said angular control means comprising an angular control rod operatively connected with said angular adjusting worm shaft extending parallel to said driven shaft and journalled in said housing sleeve, an angular control gear rotatably mounted on said angular control rod and means'for establishing a positive drive connection between said angular control rod and gear including a positive clutch and an angular control lever for engaging said clutch; and means for operating said control means comprising a source of motive power, means for reversibly driving said source of motive power, an intermediate gear coaxial with said cylinder and meshing with said angular control gear, means for driving said intermediate gear by said source including a friction clutch, and an operating lever for engaging said friction clutch.

6. A running adjusting means for a driven shaft adapted to be rotated by a gear comprising: a driving connection between said gear and said shaft, means for axially adjusting said shaft with respect to said gear and a housing sleeve secured to said gear; said axial adjusting means comprising an axial adjusting sleeve concentric within "said housing sleeve, means for angularly displac ing said axial adjusting sleeve with respect to said housing sleeve, and means for translating the angular displacement of said axial adjusting sleeve into a corresponding axial displacement of said driven shaft.

7. A running adjusting means for a driven shaft adapted to be rotated by a gear comprising: a driving connection between said gear and said shaft, means for axially adjusting said driven shaft with respect to said gear, and a housing sleeve secured to said gear; said axial adjusting means comprising'an axial adjusting sleeve concentric within said housing sleeve, means for angularly displacing said axial adjusting sleeve with respect to said housing sleeve comprising an axial adjusting worm gear integral with said axial adjusting sleeve, an axial adjusting worm coacting with said axial adjusting worm gear and an axial adjusting worm shaft connected to said axial adjusting worm, and means for translating said angular displacement into a corresponding axial displacement of said driven shaft, and means for controlling said axial adjusting means operatively connected to said axial adjusting worm shaft.

8. A running, adjusting means for a driven shaft adapted to be rotated by a gear comprising: a driving connection between said gear and said shaft, means for axially adjusting said cylinder with respect to said gear, and a housing sleeve secured to said gear; said axial adjustingmeans comprising an axial adjusting sleeve concentric within said housing sleeve, means for angularly displacing said axial adjusting sleeve with respect to said housing sleeve and means for translating said angular displacement into a corresponding axial displacement of saiddrum vcomprising ,an 1

externally threaded sleeve rotatably mounted on said drum shaft, and internal threading for said axial adjusting sleeve coacting with said externally threaded sleeve.

9. A running adjusting means for a driven shaft adapted to be rotated by a gear comprising: a

- acting with said axial adjusting worm gear, and

ment of said drum comprising an externally threaded sleeve rotatably mounted on said drum shaft, internal threading for said axial adjusting sleeve coacting with said externally threaded sleeve, said axial adjusting sleeve being fixed against axial displacement and said externally threaded sleeve being held against axial movement on said drum shaft, and means for controlling said axial adjusting means operatively connected to said axial adjusting worm shaft.

10. A running adjusting means for a driven shaft adapted to be rotated by a gear comprising: a positive driving connection between said gear and said shaft including means for angularly adjusting said drum with respect to said gear, means for axially adjusting said drum with respect to said gear, and a housing sleeve secured to said gear; said axial adjusting means comprising an. axial adjusting sleeve concentric within said housing sleeve, means for angularly displacing said axial adjusting sleeve with respect tosaid housing sleeve, means for translating said angular displacement into a corresponding axial displacement of said drum and means for controllingsaid axial adjusting means; said axial adjusting control means comprising an axial control rod, an axial control gear rotatably mounted on said axial control rod, and means for establishing a drive connection between said axial control rod and gear.

11. A running adjusting means for a driven shaft adapted to be rotated by a gear comprising: a positive driving connection between said gear and said shaft including means for angularly adjusting said drum with respect to said gear, means for axially adjusting said drum with respect to said gear, and a housing sleeve secured to said gear; said axial adjusting means compris-; ing an axial adjusting sleeve concentric within said housing sleeve, means for angularly displacing said axial adjusting sleeve with respect to said housing sleeve, means for translating said angular displacement into a corresponding axial displacement of said drum, and means for controlling said axialadjusting means; said axial adjusting control means comprising an axial control rod, an axial control gear rotatably mounted on said axial control rod, and means for establishing a drive connection between said axial control rod and gear; and means for operating said control means comprising a source of motive power, an intermediate gear meshing with said axial control gear, and means for driving said intermediate gear by said source.

12. A running adjusting means for a driven shaft and a gear for driving said shaft comprising: of a positive driving connection between said gear and said shaft including means for angularly adjusting said driven shaft with respect to said, gear, means for axially adjusting said driven shaft with respect to said gear, and a housing sleeve secured to said gear; said axial adjusting means comprising an axial adjusting sleeve concentric within said housing sleeve, means for angularly displacing said axial adjusting sleeve with respect to said housing sleeve comprising an axial adjusting worm gear integral with said axial adjusting sleeve, an axial adjusting worm coacting with said axial adjusting worm gear,

an axial adjusting worm shaft connected to said axial adjusting worm journalled in said housing sleeve, means for translating said angular displacement into a corresponding axial displacement of said driven shaft comprising an exter nally threaded sleeve rotatably mounted on said driven shaft, internal threading for said axial adjusting sleeve coacting with said externally threaded sleeve, said axial adjusting sleeve being nxed against axial displacement and said externally threaded sleeve being held against axial movement on said driven shaft, and means for controlling said axial adjusting means operatively connected to said axial adjusting worm shaft; said axial adjusting control means comprising an axial control rod operatively connected with said axial adjusting worm shaft extending parallel to the axis of said driven shaft and journalled in said housing sleeve, an axial control gear rotatably mounted on said axial control rod, means for establishing a positive drive connection between said axial control rod and gear including a positive clutch and an axial control lever for engaging said clutch; and means for operating said control means comprising a source of motive power, means for, reversibly driving said source of motive power, an intermediate gear coaxial with said driven shaft and meshing with said axial control gear, means for driving said intermediate gear by said source including a friction clutch and an operating lever for engaging said friction clutch and a reversible electric motor.

13. A running adjusting means for a driven shaft and a gear for driving said shaft comprising: a positive driving connection between said gear and said shaft including means for angularly adjusting said driven shaft with respect to said gear, means for axially adjusting said driven shaft with respect to said gear, and a housing sleeve secured to said gear; said angular adjusting means comprising an angular adjusting sleeve concentric about and keyed to said shaft, and means for changing the angular relation between said angular adjusting sleeve and said housing sleeve; said axial adjusting means comprising an axial adjusting sleeve concentric within said housing sleeve, means for angularly displacing said axial adjusting sleeve with respect to said housing sleeve, and means for translating said angular displacement into a corresponding axial displacement of said cylinder.

14. A running adjusting means for a driven shaft and a gear for driving said shaft comprising: a positive driving connection between said gear and said shaft including means for angularly adjusting said driven shaft with respect to said gear, means for axially adjusting saiddriven shaft, with respect to said, gear, and a housing sleeve secured to said gear; said angular adjusting means comprising an axial adjusting sleeve concentric within said housing sleeve, means for angularly displacing said axial adjusting sleeve with respect to said housing sleeve comprising an axial adjusting worm gear integral with said axial adjusting sleeve, an axial adjusting worm coacting with said axial adjusting worm gear, an axial adjusting worm shaft connected to said axial adjusting worm journalled in said housing sleeve, means for translating said angular displacement into a corresponding axial displacement of said driven shaft, comprising an externally threaded sleeve rotatably mounted on said driven shaft, internal threading for said axial adjusting sleeve coacting withsaid externally threaded sleeve, said axial adjusting sleeve being fixed against axial displacement and said externally threaded sleeve being held against axial movement on said driven shaft, and means for controlling said axial adjusting means operatively connected to said axial adjusting worm shaft.

15. A running adjusting means for a driven shaft and a gear for driving said shaft comprising: a positive driving connection between said gear and said shaft including means for angularly adjusting said drum with respect to said gear,

means for axially adjusting said drum with reprising an angular adjusting sleeve concentric about and keyed to said shaft, means for changing the angular relation between said angular adjusting sleeve and said housing sleeve comprising an angular adjusting worm gear integral with said angular adjusting second sleeve, an angular adjusting worm coacting with said angular 'adjusting worm gear, an angular adjusting worm shaft connected to said angular adjusting worm journalled in said housing sleeve, andmeans for controlling said angular adjusting means; said angular control means comprising an angular control rod, an angular control gear rotatably mounted on said angular control rod, and means for establishing a drive connection between said angular control rod and gear; said axial adjusting means comprising an axial adjusting sleeve concentric within said housing sleeve, means for angularly displacing said axial adjusting sleeve with respect to said housing sleeve, means for translating said angular displacement into a corresponding axial displacement of said drum, and means for controlling said axial adjusting means; said axial adjusting control means comprising an axial control rod, an axial control gear rotatably mounted on said axial control rod and means for establishing a drive connection between said axial control rod and gear.

16. A running adjusting means for a driven shaft and a gear for driving said shaft comprising: a positive driving connection between said gear and said shaft including means for angularly adjusting said drum with respect to said gear, means for axially adjusting said drum with respect to said gear, and a housing sleeve secured to said gear; said angular adjusting means comprising an angular adjusting sleeve concentric about and keyed to said shaft, means for changing the, angular relation between said angular adjusting sleeve and said housing sleeve comprising an angular adjusting worm gear integral with said angular adjusting second sleeve, an angular adjusting worm coacting with said angular adjusting worm gear, an angular adjusting worm shaft connected to said angular adjusting worm journalled in said housing sleeve, and means for .controlling said angular adjusting means; said angular control means comprising an angular control rod, an angular control gear rotatably mounted on said angular control rod, and means for establishing a drive connection between said angular control rod and gear; said axial adjusting means comprising an axial adjusting sleeve concentric within said housing sleeve, means for angularly displacing said axial adjusting sleeve with respect to said housing sleeve, means for translating said angular displacement into a corresponding axial displacement of said drum, and means for controlling said axial adjusting means; said axial adjusting control means comprising an axial control rod, an axial control gear rotatably mounted on said axial control rod, and means for establishing a drive connection between said axial control rod and gear; and means for operating said angular and axial control means comprising a source of motive power, an intermediate gear coaxial with said drum and meshing with said angular and axial control gears and means for driving said intermediate gear by said source.

17. A running adjusting means for a driven shaft and a gear for driving said shaft comprising: a positive driving connection between said gear and said shaft including means for angularly adjusting said driven shaft with respect to said gear, means for axially adjusting said driven shaft with respect to said gear, and a housing sleeve secured to said gear; said angular adjusting means comprising an angular adjusting sleeve concentric about and slidably keyed to said shaft, means for changing the angular relation between said angular adjusting sleeve and said housing sleeve comprising an angular adjusting worm gear integral with said angular adjusting second sleeve, an angular adjusting worm coacting with said angular adjusting worm gear, an angular adjusting worm shaft connected to said angular adjusting worm journalled in said housing sleeve, and means for controlling said angu-' lar adjusting means; said angular control means comprising an angular control rod operatively connected with said angular adjusting worm shaft extending parallel to said driven shaft and journalled in said housing sleeve, an angular control gear rotatably mounted on said angular control rod and means for establishing a positive drive connection between said angular control rod and gear including a positive angular control clutch and an angular control lever for engaging said angular control clutch; said axial adjusting means comprising an axial adjusting sleeve concentric within said housing sleeve, means for angularly displacing said axial adjusting sleeve with respect to said housing sleeve, comprising an axial adjusting worm gear integral with said axial adjusting sleeve. an axial adjusting worm coacting with said axial adjusting worm gear, an axial adjusting worm shaft connected to said axial adjusting worm journalled' in said housing sleeve, means for translating said angular displacement into a corresponding axial displacementof said driven shaft comprising an externally threaded sleeve rotatably mounted on said driven shaft, internal threading for said axial adjusting sleeve coacting with said externally threaded sleeve, said axial adjusting sleeve being fixed against axial displacement and said externally threaded sleeve being held against axial movement on said driven shaft, and means for controlling said axial adjusting means; said axial adjusting control means comprising an axial coning: a positive driving connection between said gear and saidshaft including means for angularly adjusting said driven shaft with respect to said gear, means for axially adjusting said driven shaft with respect to said gear, and a housing sleeve secured to said gear; said angular adjusting means comprising an angular adjusting sleeve concentric about and slidably keyed to said shaft, means for changing the angular relation between said angu lar adjustingsleeve and saidhousing sleeve comprising an angular adjusting worm gear integral with said angular adjusting second sleeve, an angular adjusting worm coasting with said angular adjusting worm gear, an angular adjusting worm shaft connected {to said angular adjustingworm journalled in said housing sleeve, and means for controlling said angular adjusting means; said angular control means comprising an angular control rod operatively connected with said angular adjusting worm shaft extending parallel to said driven shaft and journalled in said housing .sleeve, an angular control gear rotatably mounted on said angular control rod and means for establishing a positive drive connection between said angular control rod and gear including a positive angular control clutchandan angular control lever for engaging said angular control clutch said axial adjusting means comprising an axial adjusting sleeve concentric within said housing sleeve, means for angularlydisplacing said axial adjusting sleeve with respect to said housing sleeve, comprising an axial adjusting worm gear integral with said axial adjusting sleeve, an axial adjusting worm coacting with said axial adjusting worm gear, an axial adjusting worm shaft connected to said axial adjusting worm journalled in said housing sleeve, means for translating said angular displacement into a corresponding axial displacement of said driven shaft comprising an externally threaded sleeve rotatably mounted on said .drlven shaft, internal threading for said axial adjusting sleeve coacting with said externally threaded sleeve, said axial adjusting sleeve being fixed against axial displacement and said externally threaded sleeve being held against axial movement on said driven shaft, and means for controlling said axial adjusting means; saldaxial adjusting control means comprising an axial con-- 7 trol rod, operatively connected with said axial adjusting shaft, extending parallel to the axis of said driven shaft and journalled in said housing sleeve, an axial control gear rotatably mounted on said axial control rod, means for establishing a positive drive connection between said axial control rod and gear including a positive axial control clutch and an axial control lever for engaging said axial control clutch; and means for operating said angular and axial control means comprising a source of motive power, means for reversibly driving said source of motive power, an intermediate gear coaxial with said driven shaft and meshing with said angular and axial control gear, means for driving said intermediate gear by said source including a friction clutch and an operating lever for engaging said friction clutch and a reversible electric motor.

19. A running adjusting means for a driven shaft and a gear for driving said shaft comprising:

, a driving connection between .said gear and said shaft including means for angularly adjusting said shaft with respect to said gear and ahousing I sleeve secured to said gear said angular adjusting means comprising an angular adjusting sleeve concentric about and keyed to said shaft, means for changing the angular relation between said an- 

